Rotary turbine type torque converter



Aug. 24, 1954 v, E. GLEASMAN ROTARY TURBINE TYPE TORQUE CONVERTER 3 Sheets-Sheet 1 Filed Sept. 22. 1949 H l "lll 1N VEN TOR Mmmm Allg- 24, 1954 v. E. GLEASMAN ROTARY TURBINE TYPE ToEQuE CONVERTER 3 Sheets-Sheet 2 Filed sept. 22. 1949 Aug. 24, 1954 Filed Sept. 22. 1949 V. E. GLEASMAN ROTARY TURBINE TYPE TORQUE CONVERTER 3 Sheets-Sheet 3 INVENTOR.

Patented Aug. 24, 1954 UNITED STATES PATENT oFFIcE ROTARY TURBINE TYPE TORQUE CONVERTER Vernon E. Gleasman, Elmira, N. Y. Application September 22, 1949, Serial No. 117,215

, 1 i `My invention relates to hydro-kinetic :duid transmission, and more particularly `to the fluid ily-wheel type. Hydro-kinetic transmissions are not` efficient for practical purposes when same approach a 1:1 ratio, and therefore when a 1:1

12 Claims. (C1. 192-3.2)

ratio is desired a complex arrangement of i clutches and associated controls are required. Moreover, hydro-kinetic nuid ily-wheel type transmissions have definite torque limitations. These limitations are governed by the allowable sacrifice of efficiency when the fluid transmission elements are used as a fluid coupling; therefore it requires an automatic planetary or gear transmission to develop the required torque. A iluid coupling has proven to be an efficient coupling at substantially 1:1 ratio at high speeds, and the fluid transmission has proven to be eiiicient as long as there is an. appreciable ratio reduction within the range of the design.

Therefore, my invention relates to a new means of combining the well known fluid iiy-wheel type coupling with the well known fluid ily-wheel type torque converter unit, in such a manner that the design of one does not effect the efficiency or design of the other. By changing the fluid from the coupling section to the converter unit section, or vice versa, either one can beused independently of the other depending on the speed of the output shaft or load demand.

Another object of my invention is to provide a self-contained heat exchanger in my uid transmission as hereinafter set forth.

These and further objects of my invention will be set forth in the following specification, reference being made to the accompanying draw- :7

ing, it being understood that many changes may be made in the parts, and details of the construction, within the scope of the appended claims, without departing from the spirit of the invention. i

The accompanying drawings disclose one organization of the mechanical elements, in which:

Figure 1 is a longitudinal section through my novel uid transmission; and

Fig. 2 is a transverse sectional View on the line 2-2, Fig. 5, showing the automatic control.

Fig. 3 is a transverse section taken on the line 3 3, Fig.`5, showing the flyweights and collar of the automatic control.

Fig. 4 is an elevation of one of the shifting yokes.

` Fig. 5 is a view takenin the horizontal plane through Fig. 1, showing the relation ofthe pump gearing elements and the optional clutch means.

As shown, mynovel fluid transmission comprises a prime mover or driving shaft I, and a driven shaft 2, the same being preferably in axial alignment, but spaced axially apart. On the end of the prime mover shaft I is a housing 3 forming one end 0I a rotatable member having an arcuate portion 3a terminating in a peripheral annular ange 3b for the purpose hereinafter described. Preferably, the arcuate portion 3a directly carries the iiuid coupling impeller 4 consisting of an annular formation of vanes of conventional design; and on the outer periphery of arcuate portion 3a is an external starter gear 5 which may be used with the conventional starter motor of an internal combustion engine.

Secured to the ange 3b is a housing extension 6 having a complementary flange 6a secured by bolts 6:1: to iiange 3b, the housing 6 being extended to enclose the torque converter unit, and having its outer end rounded as at 6b and extending inwardly as at 6c, same terminating in a hub portion 6d which is mounted upon a hub portion la, the same being keyed thereto as vat 1b, the hub portion 'la carrying the arcuate end portion of the converter impeller l, hereinafter referred to.

As shown in Fig. 1 the hub 6d is provided on its outer end with an oil seal 10 of conventional form to prevent leakage of oil from the interior of the rotatable housing 3-6 along the fixed hollow shaft 8.

As shown, the hub portion 'la is supported by a xed hollow shaft 8 through an antifriction bearing 9, the hollow shaft 8 surrounding the driven shaft l2 and xedly entering a support IU, the same being keyed thereto as at Il. The hollow sleeve 8 is therefore non-rotatable but extends towards the prime mover shaft l and carries on its inner end within the rotatable housing a-t a spiral gear l2 for the purposehereinafter described, a bearing I3 being preferably interposed between driven shaft 2 and the inner end of hollow shaft 8, shaft 8 terminating short of the inner end of the driven shaft '2. As shown, driven shaft 2 extends into a journal 3d in the casing member 3 and is supported by an antifriction bearing I3. An oil seal may be provided betweenthe outer end of hollow shaft 8 and the driven shaft 2 to prevent leakage of oil between these parts, more particularly when support l0 does not consist of a reverse gear case.

Upon the fixed hollow shaft B within the converter impeller 'l is a portion I 4 carrying fixed, converter reactor blades l 5 secured at their outer ends to an annular tubular member it` forming the inner wall of the converter turbulence chamber, said tubular member I also carrying other fixed converter reactor blades I1, for the purposes hereinafter described.

on the inner end of shaft 2 between the emafriction bearing I8 and the inner end of hollow shaft 8 is a hub I9 having an offset portion I9a overlying the gear I2 and extending substantially to the portion I4. The outer end of the enlargement 19a is supported on the Xed hollow shaft 8 by an antifriction bearing 23. Offset portion I9a carries a complementary converter runner v2l) disposed opposite the converter impeller "I and forming one-half of the converter chamber, the other half being formed by a substantially arcuate member 2I having a flange 2 la secured by bolts o1' by welding to the flange 20a of runner 2t. As shown, the member 2I curves inwardly around the converter impeller 1 closely adjacent thereto, and also lies closely adjacent the housing extension member E19- 6c the same terminating adjacent the inner end of the hub portion 6d, leaving a small opening 22 for the purpose hereinafter described.

Carried by the runner 2t are converter runner blades and a second set cf converter runner blades 25 spaced therefrom, the runner blades 24-25 thus rotating with the driven shaft 2 at all times. This arrangement of converter runner blades 24--25 and stationary converter reactor yblades I5-I`1 and converter impeller utilize the conventional torque converter principles and need no detailed description herein. Although I have shown hollow shaft 8 held stationary, it is obvious that it may be allowed to free wheel if desired by any suitable one-way brake or locking means.

Formed integrally with the converter runner 20 are the coupling blades 26 for the fluid coupling, the same being of conventional form and consisting of an annular series of blades disposed opposite the blades 4 of the fluid coupling in the conventional manner.

In the runner 2i) between the coupling blades 26 -and the converter runner blades 24-25 are radial bores 21-28 for shafts 2S-'30, the shafts 29--30 being disposed at diametrically opposite sides of the gear I2, as shown in Fig. 2.

Mounted for rotation with the prime mover shaft I -is agear y3| (Figs. I and 5) for rota-ting gears 32 and 32a (Fig. 5) mounted'on a shaft 33 carried by and journaled in hub I9, the same directly driving a gear 34 (Fig. 2) on a clutch sleeve 35 (Fig-2), gear -32 and gear 34 being 4held in position by brackets 36-31, and sleeve 35 carrying the jaw clutch 38. In the position of parts shown in Fig. 2, the clutch teeth 38 are in mesh with the teeth 39x yon a sleeve 39 which is keyed, as at 40, to shaft 30,and hence the shaft 30 is thus directly driven by prime mover shaft I.

4Rotatably mounted upon the hub enlargement I9a is -a collar 4I carrying flyweight governors 42 and 43 which are pivoted on ears 4Ia and 4I-b of collar 4I and are urged by springs 44 and 45 into vretracted position, said flyweights having lateral projections 42:1: and 43x entering holes in said hub enlargement I9a, as shown in Fig. 3.

On the collar 4I is a lateral extension 4Ix carrying spring pressed ball 41 adapted to engage one of three detents in the hub enlargement 19a, as shown in Fig. 3. In the position shown -in Fig. 3 the sleeve 4I is inthe position in which the lyweight governors '4Z-43 are fully retracted and the shaft 30 is thus being-rotated directly'by the prime mover shaft I. When under action of centrifugal force of the rotating hub extension 19a the balls 2a-43a swing partially outwardly against the tension of springs 114-45, the detent ball 41 will engage the intermediate detent thereby shifting sleeve 39 downwardly as shown in Fig. 2` disengaging clutch member 38-3931 and engaging the jaw teeth 49 of movable clutch collar with the jaw teeth 5I which are fixedly secured to shaft 52 of a gear 53 which directly meshes with the gear I2, as shown. Consequently, the shaft 3i) would then be directly driven by the driven shaft instead of the driving shaft through gear I2, thereby rotating the shaft 30 and the conventional gear pump 55 (Fig. 1) to pass fluid through the ducts 56-51 from the iiuid coupling section into the torque converter section, as shown by the arrows in Fig. l.

When the flyweights 42-43 are further projected by centrifugal force the collar 4I will be rotated to engage the detent ball 41 (Fig. 3) in the remaining detent of the series, at which time the collar 4I will have been shifted in a rotary manner to engage the `clutch teeth 58 (Fig. 2) with the clutch teeth 59 on the shaft 60 of a gear 6I which also directly meshes with the gear I2, at which time the shaft 2-9 will be directly driven by the gear I2, the yshaft 29 carrying 'a conventional fluid pump 62 (Fig. 1) for transferring iiuid from the converter section through ducts 63 and 64 fromthe converter' section to the fiuid coupling section in the direction of the arrows.

Obviously when the clutch teeth 58-59 are engaged the clutch teeth 49-5 I, and clutch teeth 38-39cc are disengaged, and only the shaft 29r will be driven by the gear I2. A clutch fork 59a (Fig. 4) is provided for the shifting of the clutch 59 and sleeve 39 (Fig. 2f). Fork v59a is provided with a shank 591) for attaching to collar 4I (Fig. 3). In addition the collar 4I is lprovided with a detent or lock G5 (Fig. 2) `to engage between the clutch teeth 58 when in the disengaged position shown in Fig. 2. However,

when the collar 4I is rotated to engage the clutch teeth 56 with `the teeth 59 the detent `65 will have 'been shifted away from the clutch teeth 58. The object of the arrangement of the detent 55 with respect to the teeth 58 is 'to prevent the pump shaft from rotating due solely -to fluid Ypressure on the pump B2. A similar 4detent (not shown) may `be provided with respect to the pump shaft 3l] if desired. Although I have shown an'autornatic control, it is'obvious that a manual control may be utilized, separately -or in combination therewith.

By the above construction it is obvious -that when the speed ratio is approximately 1:1, the plate 2-I which rotates with the vdriven shaft 2 is rotating at approximately the same sp'eedas the plate 6b which is directly driven by the prime moverfshaft I. Therefore, if desired, -a clutch -or lock may be provided `between the parallel portions of the plates 2I and 6c (Fig. 1) `to :positively lock the same against relative rotation, thereby providing a direct `drive -feature at approximately 1:1 ratio. One form of clutch means is shown in Fig. 5 wherein 1'! isa slidable Amounted clutch collar on the hub extension of `end wall 6b. The clutch collar I-I is provided with a means to anchor the outer ends of pins 12, the inner endsof the pins being affixed to the slidable mounted clutch member 13 which is keyedwith splines 14 to end .plate 6b.y The.plate 12| is provided with internal teeth 1.5` to receive engagelgiengsof corresponding teeth 16 on clutch mem- In operation, by shifting the collar 1l to the right (Fig. 5) the clutch teeth 15 and 1B will be disengaged, and when the collar 'H is shifted to the left `(Fig. 5) the clutch teeth 'I5 and 16 will be engaged, thereby providing a positive drive. Pins 12 can be provided with conventional seals to avoid loss of fluid due to leakage around the pins. Although a jaw clutch is shownin Fig. 5, it is understood that a friction clutch might be utilized. i f

My novel above described hydro-kinetic fluid transmission constitutes a new fully automatic self-contained arrangement combining a fluid coupling and torque converter unit. 'I'his combination allows the application of true converter principles with the desired torque multiplication without handicapping the design as a fluid coupling; and also dispenses with the use of a gear transmission and by-passes the handicaps now experienced in the designing of a torque converter unit which will also act and attempt to perform the function of a fluid coupling, and therefore has definite limitations as to torque multiplication and requires an automatic transmission to supply the required torque.

It is a well known fact that a fluid transmission peaks olf at approximately 1800 to 2000 R. P. M., and `when this speed is exceededthe efficiency curve starts to decline rapidly by reason of the` interference of the stationary reactor blades, this interference becoming apparent when the converter ceases to multiply torque and approaches a 1,:1 torque transfer.

Referring to` my drawings and specification, it can be seen that the converter section can be supplied with fluid and that the iiuid coupling section willbe empty which is necessary to allow the converter section to have full control of the ratio to a point where the stationary converter reactor blades l5 and l1 cease to multiply torque and normally setup a resistance in the iiuid tract. At this point the fluid is directly transferred from the converter section as disclosed in the specification, and therefore empties the converter section so asto prevent `the stationary reactor blades I5 and l1 from setting up a resistance while the uid coupling section is in opn eration. Having control in the design of the uid transition therewill be no apparent break .in the power curve.

By an inspection of the drawings it will be noted that the torque converter section can be designed utilizing true converter principles and likewise the fluid coupling design is based on true coupling principles unaffected by the converter design, thus utilizing a proven fiuid coupling which has a high efficiency at high speeds as well as utilizing a uid transmission which has proven feasible to multiply torque up to a speed where a fluid coupling `can take over.

Referring to the drawings, associated with the coupling and converter is a iiyweight governor arrangement carried by the driven shaft member in order that the flyweights will be affected' by road speeds. The function of the governor is to select and engage the proper transition pump 55 or 62), and it is obviousthat when the pump 55 is being driven, cool uid will be pumped out of the rotating chamber D which acts as a heat exchanger by reason of the entire unit rotating as a y wheel, and being that the pump 55 continues to be driven while the converter section is utilized, consequently there will be a continuous ilow of uid through the` converter, exhausting it at the center as indicated by arrows at 22 where centrifugal `force returns it again to the periphery of chamber D. 'Ihis condition continues until such time that 'the drive shaft speed has increased to a point where the converter has reached its peak efliciency. This feature also prevents foaming. The iiyweight governors will automatically drop pump 55 and engage the opposite transition pump 62, therefore pumping the iiuid from the converter section to the fluid coupling section as disclosed. Therefore the stationary reactor blades I5 and `I'l can offer no resistance at high speed.` Consequently the fluid transmission will be as efIicient as a fluid coupling at high speed. i

I do not limit my invention to the exact form shown in the drawings, for obviously changes may be made therein within the scope of the claims.

I claim:

1. In a fluid y-wheel type transmission having a uid coupling section and a uid converter section, a drive shaft; a driven shaft axially aligned with and spaced from the drive shaft; a non-rotatable hollow shaft around the driven shaft terminating short of the inner end thereof; a closed housing to hold a quantity of fluid rotated by the drive shaft and overlying the inner ends of the driven shaft and hollow shaft and journaled on the hollow shaft, one end of the housing being pro-videdwith an annular series of blades forming the impeller of the iiuid coupling section; an arcuate impeller havingblades rotatable with the housing and disposed in the converter section; xed reactor blades on the nonrotatable hollow shaft cooperating withthe arcuate impeller; a hub on the inner end of the driven shaft within the housing carrying a portion of the converter section; a plate on the hiub portion completing the converter section and extending inwardly around the arcuate impeller between said impeller and the adjacent end of the housing, said plate terminating adjacent the hub of the arcuate impeller; spaced sets of runner blades carried by the hubs on the driven shaft and cooperating with the iixed reactor blades; other runner blades on the hub of the driven shaft cooperating with and disposed opposite the said series of coupling impeller blades; and transition means for passing the fluid from the coupling section into the converter section, and vice versa, depending on the speed of the driven shaft.

2. In a converter as set forth in claim l, a gear on the end of the hollow shaft within the housing; and said transition means comprising oppositely extending pumpshafts "at opposite sides of said gear disposed in the hub member each carrying fluid pumps disposed in ducts connecting the. fluid coupling section and the fluid converter section respectively; pinions on said shafts meshing with said gear; a collar rotatably mounted on the said hub; governorson. the collar controlling the rotary movement thereof; a normally engaged clutch on said shaft connecting the drive shaft with one of said pump shafts, said clutch disengaging when the collar is shifted; a second clutch means on said pump shaft normally disconnected from the related pinion; means actuated by initial shifting of the collar to dis'- connect the first clutch and engage the second clutch; and a third normally disengaged clutch actuated by said collar and adapted tol be engaged when thefirst and second clutches are disengaged upon further shifting of the collar.

3. In a torque converter as set forth in claim 2,

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means for preventing 'the lshaft vof the second and third clutches from rotating -by fluid pressure in said ducts when the said clutches are disengaged.

4. In a torque converter as set forth in claim 1, means for positively locking the housing and 'pla-te member together when the speed ratio is substantially 1:1.

5. In a iiuid ily-wheel type transmission having a fluid coupling section and a fluid converter section, a drive shaft; a -driven shaft axially aligned with andr spaced from the drive shaft; a non-rotatable hollow shaft faround the driven 'shaft terminating short vof the inner end thereof; a yclosed housing -to hold a quantity of fluid secured Va-tone end to the drive shaft `and overlying the inner ends of the driven shaft and hollo-w shaft, the other end of Athe housing having a hub portion journaled on the hollow shaft, `the end of the housing adjacent the drive shaft having a semi-circular recess provided with an annular series of blades forming the impeller of the huid coupling section; an arcuate inipeller having blades rotatable with the housing and disposed in the converter section; fixed reactor blades o-n the non-rotatable hollow shaft cooperating with the arcuate impeller; a hub on the inner end of the driven shaft Within the housing carrying a portion of the converter section; a plate on the hub completing the converter section and extending -inwardly .around the arcuate impeller between said impeller and the adjacent end of the housing, said plate terminating adjacent the hollow shaft; spaced sets of inner blades carried by the hub on the driven shaft and cooperating with the fixed reactor blades; other runner blades on the hub of the driven shaft cooperating with and disposed opposite the said series of coupling impeller blades; and transition means for passing the uid from the coupling section into the converter section, and vice versa.

6. In a converter as set forth in claim 5, a gear on the end of the hollow shaft within the housing; and said transition means comprising oppositely extending pump shafts at opposite sides of said gear disposed in the hub member each carrying fluid pumps disposed in ductsl connecting the fluid coupling section and the fluid converter section respectively; pinions` on'said shafts meshing with said gear; a collar rotatably mounted on the said hub; governors on the collar controlling the rotary movement thereof; Ia normally engaged clutch on said shaft connecting the drive shaft with one of said pump shafts, said clutch disengaging when the collaris shifted; a second clutch means on said pump shaft normally ldisconnected from the related pinion, means actuated by initial shifting of the collar to disconnect the first clutch and engage the second clutch; and a third normally disengaged clutch actuated by said collar and adapted to be engaged when the first and second clutches are disengaged upon further shifting of the collar.

7. In a torque converter as set forth 4in claim 6, means for preventing the shaft of the second and third clutches from rotating by fluid pressure in said ducts when the `said clutches are disengaged.

8. In a torque converter asset forth in claim 5, means for positivley locking the housing and plate member vtogether when Ythe speed ratio is substantially 1:1.

9. VIn a fluid fly-wheel type transmission having a fluid coupling sectionand'a Huid-converter section, -a drive'sha-ft; a drivenshaft axially aligned with and spaced from the drive shaft; a hollow shaft around the drive shaft terminating short of the inner end thereof; a closed rotatable housing to hold a quantity of uid secured at one end Yto the drive shaft and voverlying the inner ends of the driven shaft and'hollow shaft, the other end Vof the housing having a hub portion journaled on the hollow shaft, theend of the housing adjacent the drive shaft having a semi-circular recess provided With an vannular series of blades forming the impeller of the fluid coupling section; a hub within the housing rotatably connected with the hub portion of the housing, said hub carrying an arcuate inipeller in the converter section; fixed reactor blades mounted on the non-rotatable hollow shaft and cooperating with the arcuate mpeller; a second hub on the inner end of the driven shaft within the housing and carrying a portion forming half of the Yconverter section; an arcuate plate completing the converter section and extending inwardly around the converter impeller between the arcuate impeller and adjacent end of the housing, said plate terminating adjacent the hub which carries the'arcuate impeller; spaced sets lof runner blades carried by the second hub and cooperating with the fixed reactor blades; other runner Vblades on the second hub cooperating with and disposed opposite the coupling impeller blades of the fluid coupling section; and transition means for ypassing the fluid 'from the coupling section into 4the converter section, and vice versa, depending on kthe speed of the driven shaft.

l0. In a torque converter as set forth in claim 9, a spiral gear on the 4end of the hollow shaft within the housing; and said transition means comprising oppositely extending pump shafts at opposite sides of said spiral gear disposed in the second hub member each carrying uid pumps disposed in ducts connecting the fluid coupling section land the fluid Vconverter section respectively; pinions on said shafts meshing: with said spiral gear; a col-lar rotatably mounted Yon the second hub; fly-weight r governors on the collar controlling the rotary movement thereof; a normally engaged'clutch on said shaft-connecting the drive shaft with one of said pump shafts, said Aclutch Adisengaging when the collar is shifted; a second clutch means on said pump shaft normally disconnected from the related pinion on said pump shaft; means actuated by initial shifting of the collar to disconnect-fthe'rst clutch and engage the second clutch; and a-third normally disengaged clutch actuated by said collar and adaptedto beengagedwhenthe rst and second clutches are disengaged upon further shifting of the collar. v

-l-l. 1n a torque converter as set forth in claim l0, means for preventing the shaft of the second and third clutches from rotatingby fluid pressure in said ducts lwhen the said clutches are disengaged.

l2. vIn a torque converter as set forth in claim 9, means for positivelylocking the housing and plate member together when the vspeed ratio -is substantially 17:1.

References `Cited in the le of this patent UNITED STATES PATENTS 

